US3737142A - Rotary valve operator - Google Patents

Rotary valve operator Download PDF

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Publication number
US3737142A
US3737142A US00160696A US3737142DA US3737142A US 3737142 A US3737142 A US 3737142A US 00160696 A US00160696 A US 00160696A US 3737142D A US3737142D A US 3737142DA US 3737142 A US3737142 A US 3737142A
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Prior art keywords
lever
valve
piston
operator
slot
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Expired - Lifetime
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US00160696A
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English (en)
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H Boswell
C Partridge
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/16—Actuating devices; Operating means; Releasing devices actuated by fluid with a mechanism, other than pulling-or pushing-rod, between fluid motor and closure member
    • F16K31/163—Actuating devices; Operating means; Releasing devices actuated by fluid with a mechanism, other than pulling-or pushing-rod, between fluid motor and closure member the fluid acting on a piston
    • F16K31/1635—Actuating devices; Operating means; Releasing devices actuated by fluid with a mechanism, other than pulling-or pushing-rod, between fluid motor and closure member the fluid acting on a piston for rotating valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/02—Servomotor systems with programme control derived from a store or timing device; Control devices therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15C—FLUID-CIRCUIT ELEMENTS PREDOMINANTLY USED FOR COMPUTING OR CONTROL PURPOSES
    • F15C3/00—Circuit elements having moving parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/44—Mechanical actuating means
    • F16K31/52—Mechanical actuating means with crank, eccentric, or cam
    • F16K31/528—Mechanical actuating means with crank, eccentric, or cam with pin and slot
    • F16K31/5282—Mechanical actuating means with crank, eccentric, or cam with pin and slot comprising a pivoted disc or flap
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18888—Reciprocating to or from oscillating
    • Y10T74/1892—Lever and slide
    • Y10T74/1896—Cam connections

Definitions

  • ABSTRACT An operator for opening and closing a butterfly or other rotary valve.
  • the operator is powered by a fluid cylinder with a reciprocating piston that is connected to a lever secured to the valves stem, which lever converts the pistons rectilinear movement into rotary motion to rotate the valves flow control element between its open and closed positions.
  • the lever has an arcuate slot in the configuration of an involute curve in order that the piston s force always is applied at a right angle to the slots surfaces, thereby precluding side loads and other undesired lateral forces on the piston, lever, and valve stem from arising.
  • the operator includes a housing in which the remaining components are enclosed, and which serves as a means for mounting the operator on the body of a valve, a bearing for the levers shaft, a guide for a pin and clevis interconnecting the piston and the lever, a mount for the power cylinder, and a pressure vessel forming one end of the cylinder.
  • the operator is structured so that cylinders of various sizes can be quickly and interchangeably connected to it, thereby facilitating use of one size of operator with a wide range of line pressure and valve sizes.
  • the field of art to which the present invention pertains involves apparatus for operating valves, and more particularly to pneumatic-powered operators for opening and closing butterfly and other valves having a rotatable flow control element. From the standpoint of the United States patent classification system, the art relevant to this invention is to be found in classes 92 and 251.
  • valve manufacturers find it necessary to furnish power operators for their products, not only because valves of large size usually require something more than manual efforts to open and close them, but also because their operation from remote or central locations, or in many cases automatic operation, has come to be essential. While some valve operators are electrically powered, pneumatic power is more widely employed for butterfly and other valves with rotatable flow control elements since it provides better control at a lesser cost. Differing operating conditions, e.g.
  • an elementary or first type of known valve operator comprises an air cylinder, usually double-acting, mounted on a bracket bolted to the valves body, and with its piston connected at both ends by a clevis to a simple lever on the valve stem.
  • a second type of operator comprises a cylinder with a flanged front mount and a link connecting it to a similar stem lever, and as a variation a trunnion front mount with a clevis connecting the rod to the lever.
  • operators of a third type for use with low line pressure are actuated by double-acting or spring return diaphragm air motors, and by special double-acting air cylinders, or single-acting air cylinders with air cushions or spring return, where higher air pressure is available or larger valves are involved.
  • These are connected to the valve stems by fully enclosed oil bath rack and pinion mechanisms, or by adjustable levers and links, with or without bearings or lubricated bushings.
  • a fourth general type of operator comprises a unitized cylinder or cylinders mounted on a housing enclosing a Scotch yoke, rack and pinion, or lever and link-type mechanism which converts the longitudinal motion of the cylinders piston to ninety de- 'gree rotary motion.
  • the housing may be pressurized to act as one end of the cylinder, or it may be separated from the cylinder and filled with oil.
  • the complete assembly either fits directly on the valve stem and valve flange, or is connected to the stem and flange by open or enclosed adaptors.
  • the fourth type of operator, and the rack and pinion connecting mechanism sometimes used in it and the third type, are relatively very expensive, hence do not enjoy a ready market even though they are more durable and resistant to deterioration than the less costly devices.
  • All of the remaining foregoing mechansims impart a heavy bending load on the valve stem and a high side load on the upper portion of the stern and its bearings. These loads are the occasion of accelerated wear resulting in clearance that, with respect to butterfly valves for example, facilitates flutter of the valve disc that, in turn, can cause fretting and early complete valve failure. Clearance also results in a lag in disc position, a reduction in control sensitivity, and even incomplete shutoff in severe situations. Furthermore, the characteristic quick initial movement of the piston in.a pneumatic cylinder, due to the expansion of the air after sufficient pressure builds up to overcome static friction, causes impact where clearance is present,thus enhancing wear.
  • one object of the present invention is to provide a new rotary valve operator that includes all of the advantages of the foregoing devices, yet is less complex in structure and more versatile in use.
  • Another object of the present invention is the provision of a new type of rotary valve operator lever for converting rectilinear movement of a power piston into a rotary force for opening and closing a valves flow control element.
  • Yet another object of the present invention is the provision of a valve operator adapted to facilitate quick and easy interchange of the various sizes of pistons and cylinders used to provide it with power.
  • Still another object of the present invention is to provide a simplified pneumatic operator for rotary valves that has less moving parts, and a correspondingly greater freedom from malfunction, than other operators of similar type.
  • Another object of the present invention is the provision of an improved rotary valve operator that affords enhanced economics in manufacture and assembly without sacrifice of strength or power output characteristics.
  • the present invention comprises a fluid pressure powered operator for rotary type valves, with a lever that has a uniquely shaped slot for converting essentially the entire rectilinear force of a piston into torque that is transmitted undiminished to the flow control element of a valve on which the operator is mounted.
  • the operator includes a housing that encloses the lever and the other elements, and the housing additionally func tions as a means for mounting the operator on a valve, as a bearing for a lever shaft, as a guide for a pin and clevis that interconnect a piston and the lever, and as a mount for the pistons cylinder.
  • the housing also forms one end of the cylinder and cooperates with it to provide a double-acting fluid pressure means for reciprocating the piston in a linear path.
  • the lever is non-rotatably mounted on the valves stem, and it's shaped in the configuration of an involute curve whose circle of generation is concentric with the axis of the stern.
  • a cylindrical roller is positioned in the slot, a cylindrical pin extends coaxially through the roller and the arms of a clevis which straddles the lever, and the interior walls of the housing are provided with a pair of opposed grooves that serve to retain the pin in place.
  • the stem portion of the clevis is connected to the piston, so that rectilinear movement of the piston will effect rotation of the lever and the valve stem about the stems axis.
  • the centerline through the piston and clevis intersects the common axis through the roller and pin, and is tangent to the circle of generation of the involutely curved slot.
  • the cylinder is bolted to the housing, and the piston is similarly secured to the clevis by a bolt, to facilitate quick and easy interchange of cylinders for adapting the operator to different line pressures and valves with various operational torque requirements.
  • FIG. 1 is an isometric view of a valve operator mounted on a butterfly valve according to this invention, with portions broken away to better illustrate the operators interior components.
  • FIG. 2 is an enlarged horizontal section taken along line 2-2 of FIG. 1.
  • FIG. 3 is a transverse section taken along the line 33 of FIG. 2.
  • FIG. 4 is an enlarged side elevation of the valve operator of FIG. 1, with some portions being shown in phantom line and portions being broken away to show the internal construction.
  • FIG. 5 is a view taken along the line 55 of FIG. 4.
  • FIG. 6 is a fragmentary horizontal section showing how the valve operator of FIGS. 1-5 can be modified to accept a larger cylinder and piston.
  • a valve operator 10 comprises a housing 12 that serves, inter alia, as a means for mounting the operator on a butterfly or other rotary valve generally designated at 14, a lever 16 for converting linear force to torque for opening and closing the valves disc 18, and a clevis 20 for transmitting the rectilinear movement of a piston 22 to the lever 16.
  • the housing 12 is secured to the neck flange 24 of the valves body 26 by cap screws 28, and forms a bearing at 30 for a lever shaft 32 that is non-rotatably coupled to the valves stem 34, such as by a square or other angular shaped key or spline system (FIG. 2).
  • the lever 16 is mounted on its shaft 32, and secured non-rotatably thereto by a key 36 (FIG. 2).
  • the lever has an arcuate slot 38 in the shape of an involute curve whose circle of generation is concentric with the common axis X" of the valve stem 34 and the lever shaft 32.
  • the clevis 20 is coupled to the lever 16 by a roller 40 that is received in the involute slot 38 and is rotatably mounted between the arms of the clevis by a pin 42.
  • the interior of the housing 12 is structured to form a pair of opposed straight grooves 44 (FIGS. 3-5) in which the pin 42 travels as the operator is opening or closing the valve, the grooves 44 thus serving to retain the pin 42 in place.
  • the power for actuating the operator 10 is supplied by a pneumatic cylinder 50 that is releasably secured airtight to the housing 12 by bolts 52 and a gasket 54.
  • the cylinders piston 22 is similarly secured in a releasable manner to the neck of the clevis 20 by a bolt 56.
  • an adapter plate 60 (FIG. 6) is fastened air-tight to the housing 12 by cap screws 62 and a seal ring 64, the oversize piston 66 connectedto the clevis 20 by the bolt 56, and the oversize cylinder 68 secured in an airtight fashion to the adapter plate 60 by bolts 70 and gasket 72.
  • the lever shaft 32 is held in place in the housing 12 by a retainer ring 74 (FIG. 3), and is sealed air-tight to the housings bearing portion 30 by a pair of seal rings 76.
  • the housing 12 constitutes an air-tight vessel that functions as one end or half of a double-acting cylinder, the other half being, of course, the cylinder 50 (or 68).
  • the piston 22 (FIG. 2) will be forced to the right into the position indicated in phantom lines, causing the lever 16 to rotate clockwise approximately 90 into its new position shown in phantom, and thus opening the valve disc 18.
  • the position of the valve disc 18 at any time can be determined by means of an indicator ring (FIG. 3) that is fitted to and rotates with the valve stem 34.
  • the circle of generation of the le' vers involute slot 38 is concentric with the axis X" about which the lever and the valve stem 34 rotate.
  • an involute curve is normal to all lines tangent to its circle of generation at the points where the lines intersect the curve.
  • the roller 40, pin 42, and clevis reciprocate with the piston 22 along the center line Y, which center line is tangent to the involute slots circle of generation and therefore normal to the slot at its intersection therewith. Accordingly, the linear force of the piston 22 is exerted against the lever 16 in a direction normal thereto, regardless of whether the lever is at either end of its rotational path or at some position in between.
  • the roller 40 will exert a pulling force against the slots side 38a, causing the lever to rotate about the axis X in the direction of arrow A, and the direction of this pulling force remains normal to the side 38a as the roller 40 moves along it.
  • the roller 40 exerts a pushing force against the slots side 38b, causing the lever to rotate about axis X" in the direction of arrow B, and this pushing force continues in a direction normal to the side 38b while the roller 40 traverses it.
  • levers involute slot 38 provides a constant mechanical advantage with the piston 22, the ratio of angular travel, i.e., rotation, of the valve stem 34 and disc 18 to the linear travel of the piston 22 will remain constant, and as a result the valve can be opened or closed to any desired position, i.e., throttled, by admission of a measured amount of air pressure to the appropriate side of the piston.
  • This is a highly beneficial feature that is not obtainable with the other types of valve operator levers, as they function only through mechanical advantage that varys with respect to the air pressure against the piston as the valve stem rotates.
  • pin 42 with rounded or spherical ends is illustrated for purposes of providing a complete disclosure of one embodiment of the invention, it should be understood that the ends of the pin can be shaped in other configurations, such as cylindrical, conical and frusto-conical, with the grooves 44 shaped accordingly.
  • roller 40 is preferred, it is within the scope of this invention to eliminate the roller and enlarge the diameter of the pin 42 to also perform the rollers function.
  • valve operator be powered by a pneumatic cylinder, as any means for imparting linear reciprocating motion to the lever,'such as an hydraulic cylinder, a reversible electric motor, a single acting spring return cylinder, adiaphragm air motor, a dou', ble-ac'ting air motor, or even manual means, would be acceptable.
  • a pneumatic positioner can be connected into the pressurized air lines leading to the ports 12a, 50a to position the disc of the butterfly valve at a certain angle between open and closed.
  • a pneumatic positioner can be connected into the pressurized air lines leading to the ports 12a, 50a to position the disc of the butterfly valve at a certain angle between open and closed.
  • valve operator having increasedpossibilities of more economical manufacture since much of the more complex and expensive machining necessary in manufacture of other operators can be eliminated without adding excessive additional cost or size.
  • its flexibility for adaptation to cover a wide variety of conditions makes larger manufacturing volume, with attendant cost reduction, possible.
  • Excellent durability is another virtue of this operator, evenin spite of various severe environments in which it finds use, since it is fully enclosed. Reduction of friction and the constant mechanical advantage resulting from the unique involute configuration of the levers slot facilitate the use of cylinders with minimum bores and strokes to produce a desired torque.
  • Fail-safe operation of the operator of this invention also can be provided by any one of the various technics known in the industry, including spring return mechanisms, air cushion” systems, and elastomer or impregnated fabric diaphragm actuators, and these all can be used with solenoid, manual, or other types of air valves for on-off service and positioners for throttling applications.
  • a valve operator comprising:
  • lever rotatably mounted in the housing for nonrotatable coupling to a rotary valve stem, said lever including an arcuate slot shaped in the configuration of an involute curve whose circle of generation is concentric with the levers axis of rotation, and means for interconnecting the piston to the lever,
  • said means including a bearing element for transmitting the pistons linear force against a side of the levers slot in a direction that is normal to that side at every position of the bearing element relative thereto, said slot thereby providing a constant mechanical advantage with the piston while preventing the occurrence of a side force component on the interconnecting means, whereby when the piston is reciprocated in the chamber the linear force it exerts is converted substantially undiminished by the lever into torque about the levers axis of rotation.
  • bearing element comprises a cylindrical pin adapted to roll along the sides of the levers' slot.
  • a valve operator according to claim 1 wherein the bearing element comprises a cylindrical roller, and wherein said roller is rotatably retained between the arms of a clevis by a cylindrical pin.
  • An operator for rotating the stern ofa rotary valve comprising:
  • a lever adapted for connection to the stem for unitary rotation therewith about a common axis, means associated with the lever comprising an involutely curved surface whose circle of generation is concentric with the axis of rotation of the stem, linear actuating means including a force transmitting element, means for reciprocating the force transmitting element in a direction tangential to the circle, and
  • valve operator of claim 6 wherein the rotatable valve is a butterfly valve.
  • valve operator of claim 6 wherein the rotatable valve is a ball valve.
  • valve operator of claim 6 wherein the rotat-v able valve is a plug valve.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Analytical Chemistry (AREA)
  • Chemical & Material Sciences (AREA)
  • Theoretical Computer Science (AREA)
  • Mechanically-Actuated Valves (AREA)
  • Measurement Of Predetermined Time Intervals (AREA)
  • Coating Apparatus (AREA)
  • Nozzles (AREA)
  • Fluid-Driven Valves (AREA)
US00160696A 1971-01-20 1971-07-08 Rotary valve operator Expired - Lifetime US3737142A (en)

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Application Number Priority Date Filing Date Title
DE2102441A DE2102441C3 (de) 1971-01-20 1971-01-20 Zeitglied für binäre pneumatische Signale

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US3737142A true US3737142A (en) 1973-06-05

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US00218263A Expired - Lifetime US3737143A (en) 1971-01-20 1972-01-17 Pneumatically operated timer

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US00218263A Expired - Lifetime US3737143A (en) 1971-01-20 1972-01-17 Pneumatically operated timer

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GB (1) GB1381525A (de)

Cited By (34)

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US3878776A (en) * 1973-10-26 1975-04-22 Norwood Marking & Equipment Co Inflated bag printing device with adjustable type drive
US3933168A (en) * 1972-12-13 1976-01-20 Georg Michael Meyer Liquid closure device
JPS5377430U (de) * 1976-12-01 1978-06-28
US4280682A (en) * 1979-06-04 1981-07-28 Eaton Corporation Cam actuated butterfly valve
US4285499A (en) * 1979-03-05 1981-08-25 Eaton Corporation Cam actuated butterfly valve
US4524637A (en) * 1982-07-22 1985-06-25 Mitsubishi Denki Kabushiki Kaisha Spring-operated mechanism
US4527769A (en) * 1983-10-03 1985-07-09 Xomox Corporation Apparatus for moving a controlled member to a predetermined position
US4558605A (en) * 1983-03-11 1985-12-17 General Signal Corporation Valve actuator coupling
US4858735A (en) * 1985-06-18 1989-08-22 Heddle Richard W Stationary pivot mechanism for use with a damper
US4932631A (en) * 1986-12-16 1990-06-12 Wabco Westinghouse Fahrzeugbremsen Gmbh Apparatus to transmit drive force between two components
US5024416A (en) * 1989-06-22 1991-06-18 Sundstrand Corporation Valve actuator
US5152360A (en) * 1989-07-18 1992-10-06 Eaton Corporation Throttle cable intervention device
US5269339A (en) * 1991-06-19 1993-12-14 Szatmary Michael A Sealed bonnet for actuating a quarter turn valve assembly
US5507467A (en) * 1993-09-03 1996-04-16 Hydril Company Actuator for a drill string internal blowout preventer
US5556072A (en) * 1993-11-12 1996-09-17 Fujikin Incorporated Controller
US6170514B1 (en) * 1999-01-19 2001-01-09 Karim Esmailzadeh City water flushing and sludge prevention control apparatus
US6467498B1 (en) * 2001-08-27 2002-10-22 Karim Esmailzadeh City water flushing and sludge prevention control method
US20030226388A1 (en) * 2002-06-07 2003-12-11 Mitsuo Matsuoka Rotary drive apparatus for rotary body
US20060130898A1 (en) * 2004-12-21 2006-06-22 Karim Esmailzadeh Domestic water distribution system
EP2096267A2 (de) * 2008-02-29 2009-09-02 General Electric Company Verfahren zur Regelung des Flüssigkeitsstroms in einem Gasturbinentriebwerk
US20090217986A1 (en) * 2008-02-29 2009-09-03 Mark Douglas Swinford Methods and apparatus for regulating gas turbine engine fluid flow
US20100018587A1 (en) * 2008-07-23 2010-01-28 Honeywell International Inc. Valve adjustment assembly
WO2014139529A1 (de) * 2013-03-12 2014-09-18 Schaeffler Technologies Gmbh & Co. Kg Drehschieberanordnung
US9033778B2 (en) * 2011-12-13 2015-05-19 Controlled Holdings, Llc Barometric relief air zone damper
USD741688S1 (en) 2013-01-23 2015-10-27 Water Renu Llc Bracket with slotted side walls
WO2016033409A1 (en) * 2014-08-29 2016-03-03 A Raymond Et Cie. Fluid control valve utilizing shape memory alloy driving spring
EP3029338A1 (de) * 2014-12-01 2016-06-08 Rotork Fluid Systems S.r.l. Ventilaktuatorvorrichtung mit einem antriebsarm mit modularer struktur
US20160245189A1 (en) * 2013-11-05 2016-08-25 Mann+Hummel Gmbh Control system of at least one flap of a fluid duct and fluid duct system
US20160319849A1 (en) * 2015-05-01 2016-11-03 Fisher Controls International, Llc Adjustable travel stop for a piston actuator
US20160363221A1 (en) * 2015-06-11 2016-12-15 Hamilton Sundstrand Corporation High vibration pneumatic piston assembly made from additive manufacturing
US9636097B2 (en) 2014-07-31 2017-05-02 Tedan Surgical Innovations, LLC. Surgical retractor with a locking retractor blade
US10034662B2 (en) 2014-07-31 2018-07-31 Tedan Surgical Innovations, LLC. Surgical retractor with a locking retractor blade and swivel side arms
US20230213116A1 (en) * 2022-01-04 2023-07-06 Motomecanica Argentina S.A. Valve Actuator Device for Fluid Flow Control
US11927249B2 (en) 2019-04-30 2024-03-12 Woodward, Inc. Compact linear to rotary actuator

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US4112823A (en) * 1975-12-17 1978-09-12 Carrier Corporation Methods and apparatus for controlling an hydraulic cylinder
US4997160A (en) * 1990-06-08 1991-03-05 Grumman Aerospace Corporation Ball lock control valve actuation plunger - hydraulic type
CN106151655B (zh) * 2016-08-28 2019-08-13 北京凌天世纪控股股份有限公司 自动断水保护装置

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US3385120A (en) * 1966-07-06 1968-05-28 Rotork Eng Co Ltd Auxiliary drive unit for an actuator
US3460799A (en) * 1967-08-25 1969-08-12 Robert E Sanctuary Variable torque valve actuator
US3650506A (en) * 1970-06-26 1972-03-21 Us Industries Inc Rotary valve with line pressure connected actuator

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US3261266A (en) * 1963-12-31 1966-07-19 Ledeen Inc Valve actuator
US3298286A (en) * 1964-12-18 1967-01-17 Grove Valve & Regulator Co Valve operator
US3385120A (en) * 1966-07-06 1968-05-28 Rotork Eng Co Ltd Auxiliary drive unit for an actuator
US3460799A (en) * 1967-08-25 1969-08-12 Robert E Sanctuary Variable torque valve actuator
US3650506A (en) * 1970-06-26 1972-03-21 Us Industries Inc Rotary valve with line pressure connected actuator

Cited By (45)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3933168A (en) * 1972-12-13 1976-01-20 Georg Michael Meyer Liquid closure device
US3878776A (en) * 1973-10-26 1975-04-22 Norwood Marking & Equipment Co Inflated bag printing device with adjustable type drive
JPS5377430U (de) * 1976-12-01 1978-06-28
JPS5831012Y2 (ja) * 1976-12-01 1983-07-08 株式会社ナブコ 建物用ダクトにおけるダンパの開度調節機構付流体圧式駆動装置
US4285499A (en) * 1979-03-05 1981-08-25 Eaton Corporation Cam actuated butterfly valve
US4280682A (en) * 1979-06-04 1981-07-28 Eaton Corporation Cam actuated butterfly valve
US4524637A (en) * 1982-07-22 1985-06-25 Mitsubishi Denki Kabushiki Kaisha Spring-operated mechanism
US4558605A (en) * 1983-03-11 1985-12-17 General Signal Corporation Valve actuator coupling
US4527769A (en) * 1983-10-03 1985-07-09 Xomox Corporation Apparatus for moving a controlled member to a predetermined position
US4858735A (en) * 1985-06-18 1989-08-22 Heddle Richard W Stationary pivot mechanism for use with a damper
US4932631A (en) * 1986-12-16 1990-06-12 Wabco Westinghouse Fahrzeugbremsen Gmbh Apparatus to transmit drive force between two components
US5024416A (en) * 1989-06-22 1991-06-18 Sundstrand Corporation Valve actuator
US5152360A (en) * 1989-07-18 1992-10-06 Eaton Corporation Throttle cable intervention device
US5269339A (en) * 1991-06-19 1993-12-14 Szatmary Michael A Sealed bonnet for actuating a quarter turn valve assembly
US5287881A (en) * 1991-06-19 1994-02-22 Szatmary Michael A Sealed bonnet for actuating a quarter turn valve assembly
US5507467A (en) * 1993-09-03 1996-04-16 Hydril Company Actuator for a drill string internal blowout preventer
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Also Published As

Publication number Publication date
DE2102441A1 (de) 1972-08-03
US3737143A (en) 1973-06-05
GB1381525A (en) 1975-01-22
DE2102441B2 (de) 1974-11-07
DE2102441C3 (de) 1975-06-12

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